Reversible clutch for hydraulic power mechanism



Aug. 11, 1953 F. w. KRUEGER REVERSIBLE CLUTCH FOR HYDRAULIC POWERMECHANISM l m N\ Q 3 m, Q m m |.l a h l S 4 WN NN QM m R q A wN WN .W. Wh 1 w- 2 ll Q Q Q Q m.| r

2 ,1 Nm 0 mm 0 5 9 l L l w S a d T m k e l i F 0 INVENTOR .2 bank ZZZJCnLeyar BY M M ATTORNEYS Aug. 11, 1953 F. w. KRUEGER 2,643,416

REVERSIBLE CLUTCH FOR HYDRAULIC POWER MECHANISM Filed Sept. 11, 1950 4Sheets-Sheet 2 INVENTOR Fran k w lnz e981" ATTORNEYS Aug. 11, 1953 F. w.KRUEGER REVERSIBLE CLUTCH FOR HYDRAULIC POWER MECHANISM 4 Sheets-Sheet 3Filed Sept. 11. 1950 INVENTOR Frank Zak/mega!" ATTORNEYS 1953 F. w.KRUEGER 2,648,416

REVERSIBLE CLUTCH FOR HYDRAULIC POWER MECHANISM Filed Sept. 11, 1950 4Sheets-Sheet 4 27 VIII/[WWW INVENTOR Frank 2D .76zuegez' BY W ATTO R NEYS Patented Aug. 11, 1953 REVERSIBLE CLUTCH FOR HYDRAULIC POWERMECHANISM Frank W. .KruegenSaratoga, Califi, assignor to Bee-GeManufacturing C0,, 'Gilroy, Cali'f., a cor- ,porationoi CaliforniaApplication September 11, 1950., .SerialsNmlS iflGO 1 Claim. l

This'invention 'is'directed to, and it is a major 'object to provide, anovel mechanism operative to convert hydraulic pressure intosubstantially constant rotary motion; the mechanism, in effect, being afluid motor.

Another important object of the invention is to provide a --hydraulicpower mechanism which ineludes, in :novel combination, a hydraulic powercy-linder caused to reciprocate by means of an -automatic reversingvalve unit, and a double-acting dual rack. and pinion assemblyreciprocated by the power cylinder and mounted in driving relation .on amain shaft; the ar .ngement being compactysturdy, and ,positive inoperation.

eAfurtherobject of the invention is to provide a hydraulicpower(mechanism, as in the preceding paragraph, which includes a rotaryoutput .member, such as a sprocket, urnaole on the main shafaanda'hydraulically actuated clutch interposed between the main shaft andsaid rotary output member; there being a manual control valve arrangedto control operationof the power ,cylinderand clutch.

An additionalobject or" the invention is to provide a hydraulic powermechanism which is Well vadaptedbutnotlimited, for to propel animplement,such a rotary ditcher, forcefully along the ground at a veryslow rate of travel; i. e. to cause the implement to creep at arelatively constant speed.

It is also an object of the invention to-provide a hydraulic powermechanism, of the type described, wherein'the included double-actingdual rack-and ,n assembly ernhodies a .novel reversing device wherebythe driven shaft can be caused to rotate one direction or the other,selectively.

Still another object of the invention is to provide a practical andreliable hydraulic power .mechanism,and,yet one which will beexceedingly effective for the purpose for which is designed. Eheseobjects are accomplished by means oi such structure and relativearrangement of parts as will fully appear by'a perusal of the following5 is a fragmentary elevation .of themain .shaf-t'dctached; the viewshowing the .portion of the .-shaf.ts with which the double-acting dualrack-and pinion assembly cooperates.

Fig.6 is aplan view of therollershifting cage, detached.

Fig. '7 is a sectional elevation of the same.

Fig. t is a diagram 'of the hydraulic pressure system.

Referring now more particularly .to the char- .a-cters or reference onthe drawings, the novel, hydraulic-power mechanism comprises a housing,indicated generallyat l, which housing includes end heads .2:and 3, .andside plates 3 and 5.

.-A horizontal mainishaftiii extends transversely through the housing i,being journaled in connection with the .sideplates 4 .and fi by means ofbearings l associated with appropriate seals, as shown.

The main shaft 6 projects some distance beyond theside plate :5, :and afinal drive member, .here in he 'formeof a. sprocket 8, is turnable onsaid projecting portion of the shaft; there being a hydraulicallyactuated clutch assembly, indicated generally at :Q, interposed betweensaid projecting portion of the-shaft and the-sprockets.

Thecl-utCh assembly -9 includes tapered selfretracting dogs Ba adaptedto be'advanced by .a spring-cushioned hydraulic pressure fed theretothrough-the medium of afitting l2.

Upon entry :of hydraulic pressure into the cyl- .in'der =5 l, the-pistonvia advances to advance the clutch dogs LG, whereby the mainsha-ft :S isthen connected in driving relation to the sprocket 8.

.A hydraulic power :cylinder i3 is mounted in connection with, andprojects from, the end'head 2,..horizontally, with rtheaxisof the powercylinder-inrthesarne vertical plane as the axis of the :mai-n'shaf-t but.at right angles thereto. The ydr-aulic power-cylinder includes a pistoni i, and a connecting rod it which slldably projects through a suitablepaclting'gland it in the end head .2; the free end .of the connectingrod i5 being coupled, as at ll, to a cross head it disposed in thehousing .I. This cross head is included in a double-"acting, dual rackand pinion assembly, indicated generally at 1'9, which is employedbetweenthe connecting rod 'itiand the main shaft 6 to 'causesubstantially constant rotary motion of the latter'upon reciprocationofthe'piston i i.

The double-acting, dual rack and pinion assembly 19"comprises, tog-etherwiththe cross head 18, apair of opposed racks 2 0 which project from--'sa-idcross head in space'cl parallel relation,passmg the main shaft 5on opposite sides thereof.

The racks'ZD, whilc parallel to the axis of the connecting rod |5, arelaterally offset relative to each other, and run in mesh withcorresponding pinions 2| turnable on a cage 22, which is in turn mountedon an enlarged portion 23 of the main shaft 5. The racks 2B are held inmesh with the pinions 2| by suitably mounted rollers R.

The following automatic clutch device is em-- ployed between each pinion2i and the enlarged portion 23 of the shaft 6; the clutch arrangementbeing such that upon one stroke of the racks one pinion drives theshaft, while on the other stroke of the racks the other pinion drivesthe shaft; the pinion which is not clutched in driving relation to theshaft overrunning in each instance. This is accomplished as follows:

The enlarged portion 23 of the shaft 6 is formed with a plurality ofcircumferentially spaced clutch fiats 24, and the cage 22 is fitted, incorresponding circumferentially spaced relation, with a plurality ofpairs of clutch rollers 25, with the rollers of each pair in end to endrelation and disposed in slots 26. The rollers 25, as carried by thecage 22, thus lie between the corresponding clutch flats 24 and theinner periphery of the pinions 2|; each circumferential row of therollers 25 lying within the radial plane of the corresponding pinion 2|.

The cage 22 is normally disposed so that the rollers 25 are adjacent oneside of the corresponding clutch fiat 24, whereby each pinion 2|, whenrotated in one direction, causes the corresponding clutch rollers 25 togrip and drive the main shaft 6, overrunning in the opposite direction.As the pinions 2| are reversely actuated with each stroke of the rackscaused by the hydraulic power cylinder l3, the described clutchingarrangement causes said pinions 2| to impart a substantially constantdrive to the main shaft 6; one pinion working while the other overruns,and vice-versa.

It will be recognized that upon part-rotation of the cage 22, whereby todispose the clutch rollers adjacent the opposite side of thecorresponding clutch fiat 24, the clutch arrangements will function inreverse, with consequent reverse drive of the main shaft 6 uponreciprocation of the racks 20 by the hydraulic power cylinder 13. Suchpart-rotation of the cage 22 is accomplished as follows:

Adjacent the side plate 4 the cage 22 is formed with an end hub 2!having a diagonal slot 28 therein. A shifting rod 29 is axially slidablydisposed in a. bore 30 which opens to the adjacent end of the main shaft6 said rod 29 being adapted to be axially shifted by an externallymounted lever 3|.

A radial pin 32 having a turnable bearing sleeve 33 thereon projectsradially from the shifting rod. 29, through an elongated slot 34 in theshaft 6, and thence extends into the diagonal slot of the hub 21 on cage22. Thus, by shifting rod 29 by lever 3|, the radial pin 32 and thebearing sleeve 33 work in the diagonal slot 28 to cause a partturn ofthe cage 22.

As the cage 22 is rotated from one position to another, the alined pairsof clutch rollers 25 are adjusted from a position adjacent one side ofthe corresponding clutch fiat 22 to a position adjacent the other side,so as to reverse the clutching and overrunning action between eachpinion 2| and the main shaft 6. With this arrangement, eifectivereversal of the power mechanism between the hydraulic power cylinder l3and. final drive sprocket 8 is attained without startingor stopping thepower cylinder l3, and without in any way affecting the normal operationof the latter, which is as follows:

The hydraulic power cylinder I3 is caused to reciprocate by means of anautomatic reversing valve unit, indicated generally at 35. The valveunit 35 comprises a valve body 36, in the housing formed with a bore 31which extends axially parallel to the path of motion of the racks 20.

A dual piston valve 38 is mounted in the bore 37 for reciprocation, suchvalve 38 being adapted to alternately feed hydraulic pressure from asupply port 39 to feed ports 40, which are connected by ducts 4| and 42to opposite ends of the hydraulic power cylinder l3. Also, the valve 38uncovers the opposite pressure relief or exhaust port 43 as pressure isfed to one of the feed ports 45. Hydraulic pressure is delivered to theport 39 by a conduit 44 of a hydraulic pressure supply system, as shownin Fig. 8, and which will hereinafter be described in greater detail.

The valve 38 is yieldably held in its alternate working positions by aroller-type, spring-pressed detent 45 working in cooperation with anotched holding plunger 46 which is an extension of one end of saidvalve, and which plunger rides in the bore 37.

The valve 38 is reciprocated in the bore 31, with proper timing, by alateral finger 41 which projects from one of the racks 20, and a controlrod 48 extends through such lateral finger in slidable relation; suchcontrol rod 48 being an axial extension of the valve 38 and having stopshoulders S between which finger 41 moves.

Compression springs 49 surround the control rod 48, one between thelateral finger 41 and the valve 38, and another between said finger 41and a stop nut assembly 50 on the end of the rod opposite said valve.There is considerable play between the springs and the lateral finger41, as shown. The result is that as finger 4? moves in one direction, itfinally engages the adjacent stop S, and then shifts rod 48 itself untilplunger it has fully raised roller 45 out of one notch, at which pointfinger 41 has reached the end of its stroke. In the meantime however,the related spring 49 has been compressed, and when the roller 45 hasbeen lifted out of one notch as above stated, said spring suddenly actsto further advance rod 48 to place roller 45 in the other notch ofdetent 46. Valve 38 is thus reversed only as the racks 20 aresubstantially at the end of the corresponding stroke The result is thatthe valve unit 35 is reversed, with proper timing, to cause constant andsmooth reciprocation of the hydraulic power cylinder I3.

The hydraulic pressure supply system, which is employed in connectionwith the described hydraulic power -.mechanism, is showndiagrammatically in Fig. 8.

The numeral 5| indicates a fluid reservoir, which reservoir may be thehousing or a tank to which said housing opens. In this connection it isto be noted that the pressure relief or exhaust ports 43 deliverdirectly into the housing i, but for the purpose of illustration thediagrammatic system in Fig. 8 is shown with a return conduit 52.

A hydraulic pressure feed conduit 53 leads from the reservoir 5|, havinga hydraulic pump 54 interposed therein, together with a hand valve 55.

Beyond the pump 54 the hydraulic pressure feed conduit 53 feeds to andfrom a manual control valve 58, and beyond said valve the conduit 53branches, one branch 51 leading to the cylinder ll of the hydraulicclutch assembly 9, while the other branch, which is the conduit 44,leads to the automatic reversing valve 35.

The manual control valve 56 is a double-piston, three-position valve, asshown, and there are conduits 58 which lead from said control valve tothe return conduit 52. The control valve 56 may be set in one position,as illustrated, to feed hydraulic pressure to the power cylinder l3 andclutch assembly 9, so as to cause said cylinder to function and theclutch to be engaged simultaneously.

A pre-loaded check valve 59 in the conduit 55 is employed to the endthat the clutch assembly 9 engages slightly in advance of the powercylinder 13 beginning to operate.

In another position both said piston and clutch assembly areinoperative, and the hydraulic pressure from the pump vents to thereservoir, as well as bein vented back from the conduit 53.

In an intermediate position of said valve high pressure is held orlocked up in the conduit 53 beyond the valve 56, whereby to maintain theclutch assembly 9 engaged, but without the power cylinder 53functioning.

With the described hydraulic power mechanism hydraulic pressure isconverted effectively and positively into substantially constant rotarymotion; the device working smoothly and forcefully. employed inconnection with a tractor mounted rotary ditcher and serves to converthydraulic pressure from the tractor pump to rotary motion of the finaldrive sprocket 8; the latter being chain-connected to the tractor axleto cause the tractor to creep forward slowly, as is requisite for properoperation of the ditcher.

The ditcher is driven from the power take-off shaft of the tractor, andrequires the tractor engine to be operated relatively fast, and fasterthan the desired ground speed which would automatically result. Hence,the herein described hydraulic power mechanism is employed to convertthe available hydraulic pressure to creeping motion of the tractor.

From the foregoing description it will be readily seen that there hasbeen produced such a device as substantially fulfills the objects of theinvention, as set forth herein.

While this specification sets forth in detail the In one adaptation ofthe device it is present and preferred construction of the device, stillin practice such deviations from such detail may be resorted to as donot form a departure from the spirit of the invention, as defined by theappended claim.

Having thus described the invention, the following is claimed as new anduseful, and. upon which Letters Patent are desired:

In a power mechanism which includes a rotary shaft and a rotary memberconcentric with and through which the shaft projects; a reversibleclutch connection between the shaft and member and comprising a cageturnable on an intermediate portion of the shaft and on which the rotarymember is turnably supported, a hub projecting from the cage andturnable on one end portion of the shaft ahead of said intermediateportion and the rotary member, reversible clutch connection meansbetween the cage and shaft and actuated upon rotation of the cagerelative to the shaft, means to so rotate the cage including a rodslidable in said end portion of the shaft and projecting therefrom forpush-pull manipulation, a casing enclosing the cage, rotary member andhub and in which the shaft beyond the hub is journaled, a lever outsidethe casing and disposed at right angles to the rod, a pivotal mount forthe lever on the casing, and a connection between the rod and lever toslide the rod upon reciprocation of the lever.

FRANK W. KRUEGER.

References Cited in the file of this patent UNITED STATES PATENTS NumberName Date 236,310 Dees Jan. 4, 1881 549,118 Faulkner Nov. 5, 18951,078,151 Lamb Nov. 11, 1913 1,163,803 Bickford Dec. 14, 1915 1,195,520Snideman Aug. 22, 1916 1,375,711 Lower Apr. 26, 1921 1,437,120Stephenson Nov. 28, 1922 1,692,771 Ferris Nov. 20, 1928 1,927,046 PowellSept. 19, 1933 1,976,791 Ljungstrom Oct. 16, 1934 2,497,608 Herrstrum eta1 Feb. 14, 1950

